Hydraulic power winch



Nov. 19, 1968 F. D. POOLEY, JR 3,411,751

HYDRAULI C POWER WINCH Filed April 20, 1967 5 Sheets-Sheet l Fig .9

INVENT'OR. FRANK D. POOLEY,,JR.

ATTORNEYS.

19, 1968 F. D. POOLEY, JR 3,411,751

HYDRAULI 0 POWER WINCH Filed April 20, 1967 5 Sheets-Sheet 5 1 t 67 63 69 M 66 i; L560 12: 1?

INVENTOR. 75b FRANK D. POOLEY,JR.

I Fig. 4 BY Wv-W ATTORNEYS.

Nov. 19, 1968 F. D. POOLEY, JR 3,411,751

HYDRAULIC POWER WINCH Filed April 20, 1967 5 Sheets$heet 4 1 N VEN TOR.

FRANK D. POOLEY,JR.

ATTORNEYS.

Nov. 19, 1968 F. D. POOLEY, JR 3,411,751

HYDRAULIC POWER WINCH 1 Filed April 20, 1967 5 Sheets-Sheets INVENTOR. FRANK D. POOLEY, JR.

WVW

ATTORNEYS.

United States Patent 3,411,751 HYDRAULIC POWER WINCH Frank D. Pooley, Jr., 1936 Paper Mill Road, Huntingdon Valley, Pa. 19006 Filed Apr. 20, 1967, Ser. No. 632,370 8 Claims. (Cl; 254-150) ABSTRACT OF THE DISCLOSURE A reversible hydraulic motor is fixedly mounted in a housing and has a shaft extending from one end thereof. A capstan is mounted for rotation about said motor and housing. A gear is keyed to the shaft of the motor for rotation therewith and for axially sliding thereon. The inner radial side of the gear is attached to one half of a ratchet mechanism for engaging the other half of the ratchet mechanism attached to the housing. The gear teeth enage mating teeth on the inner cylindrical surface of the capstan for rotating the capstan and are disposed for axial sliding engagement therewith. A hydraulic cylinder is positioned in one of the hydraulic fluid lines to the reversible hydraulic motor, said cylinder containing a piston and rod which are attached to a mechanism for engagement with said gear and ratchet mechanism whereby when the reversible hydraulic motor is turning the capstan in one direction the ratchet will prevent rotation in the opposite direction, and when the motor is reversed, the hydraulic cylinder and piston arrangement will release the ratchet mechanism and the motor will rotate the capstan in the other direction, and further, the hydraulic cylinder and piston arrangement may disengage completely the gear from the capstan so that there is no connection between the motor and the capstan. Hand actuated mechanical means may be provided to disengage the capstan and gear in the event of a failure in the hydraulic system.

Background of the invention The present invention relates to hydraulically operated winches, and more particularly, to a winch or capstan which consists of a housing containing a stationary hydraulic motor and having a rotatable drum mounted thereon and engaging said motor, which drum is attached to the halyard of the sail on the boat for raising and lowering the sail by means of a remotely controlled clutch.

In the prior art, hydraulic motors have been used in conjunction with capstans or winches. The devices produced have been complicated and expensive to manufacture'rThe problems in both manufacture and operation, as well as performance have been manifold.

In particular, the prior art has not provided a reversible hydraulically actuated capstan to raise the sail and hold it at any position which includes a built-in fail-safe feature to prevent the sail from falling, and which is capable of lowering the sail at a controlled rate, or providing a freefall in the alternative, and further, which accomplishes all this remotely from the cockpit of the sailing vessel. Further, should the machine fail to function hydraulically, means must be provided both to prevent the sail from falling and to permit the sail to fall in the event that this is desired. I

Summary ofthe invention The present invention provides an operative, desirable solution to the problems presented in the prior art. It comprises a capstan drum rotatably mounted on a housing containing a reversible hydraulic motor fixedly connected to the housing. A gear is disposed on the motor shaft for rotation therewith, said gear having teeth engaging mating teeth on the capstan drum for driving said drum. The gear is disposed to slide axially on the shaft to positions in 3,411,751 Patented Nov. 19, 1968 full and partial engagement with the mating teeth on the capstan, as well as to a position free of engagement with the capstan drum. The gear is provided with a ratchet mechanism to prevent rotation in one direction when the gear is in full engagement with the capstan drum and the motor is rotating the drum in the opposite direction, which ratchet mechanism, as well as the gear itself, is positioned hydraulically by means of a piston and cylinder arrangement remotely controlled and in communication with the hydraulic fluid supply lines to the motor.

In the preferred embodiment of this invention, mechanical means are provided to raise the gear and disengage the ratchet mechanism in the event that the hydraulic apparatus fails to function.

Accordingly, an object of this invention is to provide a hydraulically operated capstan system for remotely controlling the raising and lowering of a sail on a sailing vessel.

Another object of this invention is to provide a hydraulically operated capstan apparatus having a reversible hydraulic motor, gear and clutch means disposed within the capstan, and capable of remote actuation.

Another object of this invention is to provide a novel gear and ratchet apparatus for use with a hydraulically operated capstan apparatus which is hydraulically and remotely controlled.

Another object of this invention is to provide a novel mechanical actuation means for the gear and clutch mechanism of a hydraulically operated self-contained capstan apparatus.

Brief description of the drawings FIG. 1 is a diagrammatic representation of .a hydraulic system in accordance with the preferred embodiment of this invention;

FIG. 2 is a central vertical section of the capstan shown in FIG. 1;

FIG. 3 is a vertical section taken along the line III-III of FIG. 2;

FIG. 4 is a partial vertical elevation of a portion of the internal parts of the capstan taken along the line IV-IV in FIG. 3, and showing the gear of the capstan in phantom alternate position;

FIG. 5 is a cross section taken along the line V-V of FIG. 2;

FIG. 6 is an end view taken along the line VIVI of FIG. 2;

FIG. 7 is an exploded view in perspective of a number of the internal parts of the capstan shown in the previous figures with a portion of the gear shown in section;

FIG. 8 is a plan 'view of the face portion of the ratchet mechanism used in this invention; and

FIG. 9 is a section of a portion of the gear teeth taken along the line IX-IX in FIG. 3.

Description of the preferred embodiment Although specific forms of the invention have been selected for illustration in the drawings, and the following description is drawn in specific terms for the purpose of describing these forms of the invention, this description is not intended to limit the scope of the invention which is defined in the appended claims.

FIG. 1 shows diagrammatically, the remote control hydraulic capstan system in accordance with the preferred embodiment of this invention. The pump 10 is mounted in the engine room of the vessel and is connected by means of the coupling 11 to an engine or motor 12 of any conventional type. The pump has a fluid inlet 13 for receiving hydraulic fluid from a reservoir 14. The discharge outlet 15 of the pump 10 communicates by suitable conduit means 16 to a multiport, m'ultidirectional valve 17 which is conveniently disposed in the cockpit of the sailing vessel. The valve communicates by suitable conduit means and 21, respectively with the capstan, designated generally 30, which conduit means function as both supply and return lines for hydraulic fluid for the motor in the capstan (to be described more fully hereinafter). The valve 17 has a return line 22 to the fluid reservoir 14, for returning fluid from the lines 20 or 21 as appropriate, or for recirculating fluid from the line 16.

The capstan has a line or halyard 25, which is fixedly connected at one end to the capstan so as to be wound thereon, said line being connected at the other end to the sail of the sailing vessel for raising and lowering said sail.

Referring to FIG. 2, the capstan 30 as shown comprises an outer rotatable portion or drum 31 which is mounted for rotation about the housing 32. The housing 32 may be fixed to the deck or other suitable stationary portion of the vessel, such as the mast, as by means of bolts (not shown) passing through the bolt holes 33 on the base 34 of the housing 32, as more clearly shown in FIG. 6. Mounted within the housing 32 (FIG. 2), is a reversible hydraulic motor 35, of a conventional type which is well known in the art. The casing 36 of the motor .35 is securely fastened to the vertical portion 37 of the housing 32 by any suitable means (not shown). A shaft 38 extends from one end of the motor 35. The hydraulic motor is reversible such that the shaft may be rotated by the motor in either direction depending on the manner in which hydraulic fluid is supplied to the motor. For this purpose the motor has two ports 26 and 27 each of which can function as an inlet or exhaust port. Port 26 communicates with hydraulic fluid passage 23 in housing 32 which is connected to conduit means 20; and port 27 communicates with hydraulic fluid passage 28 in housing 32 which communicates with hydraulic cylinder 94; the cylinder 94 communicating with the hydraulic fluid passage 24 in housing 32, which is connected to conduit 21. The disposition of the ports in the cylinder 94 will be discussed hereinafter. When hydraulic fluid under pressure is supplied through conduit 20 and port 26, it passes through the motor and rotates the shaft in a counterclockwise direction (when viewed from the top in FIG. 2), and passes out the discharge port 27 and thence through the conduit 21. Were the direction of the fluid in these lines to be reversed, the direction of rotation of the motor would likewise be reversed.

The shaft 38 passes through a clearance hole 39 in the plate 40 which is fixedly attached to the vertical portion 37 of the housing 32 by any suitable means (not shown). The shaft 38 has an annular groove 3812 near its outer end which is juxtaposed with the annular slot 18 formed between the mating plates of the dome of the capstan drum 31. Disposed in the groove 38a and the slot 18 is a snap ring 19 for axially retaining the drum 31 on the shaft 38.

Between the plate 40 and the inner cylindrical surface 41 of the drum 31, is a bearing 42 composed of nylon or other suitable, low friction material, which is held in fixed engagement with the inner cylindrical surface 41 by any suitable means, such as adhesive. A bearing 43 of similar material is aflixed to the cylindrical surface 44 of the drum 31 and contacts the outer cylindrical surface 45 of the stepped portion of the housing 32. Further bearing surfaces are provided in the base portion 34 of the housing 32 by the plurality of solid cylindrical bearing slugs 46 which are spaced about the base 34 in fixed engagement therewith and which are composed of a suitable bearing material such as bronze. The slugs 46 are disposed in the base portion 34 to protrude above the base to contact the bottom annular surface 47 of the capstan drum 31.

Mounted on the end of the shaft 38, there is a gear 50 which is in close sliding engagement with the shaft and which is keyed to the shaft by means of the key 51. In this manner the shaft 38 will cause the gear 50 to rotate, and the gear can be moved axially along the shaft.

Around the periphery of the gear, are spaced the gear teeth 52, shown in greater detail in FIG. 4. The gear teeth 52 engage mating teeth 53 disposed on the inner cylindrical surface of the drum 31. Suflicient room is left between the outer radial surface 54 of the gear 50 and the inner surface of the dome 55 of the drum 31, so that the gear 50, when it is slid axially outwardly along the shaft 38 may be completely disengaged from the mating teeth at 53 on the drum 31, as shown in FIG. 3. The gear 50 in this position will turn freely with the shaft 38 and will not engage the drum 31 a all. The mechanism for raising and lowering the gear 50 will be described below following a description of the fail-safe ratchet mechanism.

Referring to FIGS. 2, 3 and 8, the fail-safe ratchet mechanism is shown in greater detail. It comprises an annular body portion 61 having teeth 62 disposed radially outwardly from the center thereof, on the radial face thereof. The body portion 61 has an annular flange portion thereon 63, which is keyed for rotation to the gear 50 in the annular slot 64 by the keys 65. (See FIG. 5.) A plurality of springs 57 are disposed in the slot 64 between the gear 50 and the annular flange 63. The springs 57 are spaced from one another and are retaining in wells 58 and 59 in the gear 50* and the annular flange 63, respectively, and serve to exert a force against the body portion 61 to force it out of the annular slot 64. A- retaining ring 66 is fastened by any suitable means, as for instance by machine screws 67, to the underside of the gear 50. The retaining ring 66 extends along the underside of the gear 50 and across a portion of the opening formed by the annular slot 64, and still further across a portion of the annular flange 63 to retain the flange 63 in the slot 64.

The remaining elements in the ratchet mechanism 60 comprise a second annular body portion 68 which is aflixed to the upper portion of the plate 40 by any suitable means (not shown). The body portion 68 has ratchet teeth 69 extending radially on the surface thereof from the center thereof and formed to mate with the teeth on the body portion 61, so that when the two portions are mated as in FIG. 2, the teeth are fully engaged. In this position the gear 50 will be held against rotation in the clockwise direction (when viewed from the top FIG. 2) while being permitted to rotate in the counterclockwise direction. As shown in FIG. 2, if the gear were to rotate in a counterclockwise direction the annular body portion 61 would be raised vertically by virtue of the action of the sloping sides of the mating teeth 62 and 69 on the body portions 61 and 68, respectively as portion 61 is rotated with respect to portion 68. The annular flange 63 is yieldably retained in the annular slot 64 against retaining ring 66- by the springs 57, and a clearance space 70 is provided between the annular flange 63 and the gear 50', to allow the body portion 61 to rise. If the gear were to attempt to rotate in a clockwise direction (when viewed from the top in FIG. 2), the springs 57 would force the teeth to remain in engagement and prevent rotation.

Referring to FIGS. 2-7, I will now describe the clutch mechanism. FIG. 7 shows an exploded view of the individual elements comprising the clutch mechanism. The mechanism works by either hydraulic or mechanism means to raise the gear 50 sufliciently to disengage the ratchet mechanism 60, and to raise the gear 50 further to throttle the descent of the sail, and to raise the gear still further so that it is disengaged from he drum 31 and allows the sail to fall freely. The gear 50 has a radially recessed body portion 56 which extends axially inwardly toward the motor 35 and contains a peripheral annular groove 71. Retaining rings 72a and 72b each have a protruding lip 73m and 7311 which engages the annular groove 71 for sliding engagement therewith when the gear is rotated. The two sections 72:: and 72b, when placed in full engagement with the annular groove 71 in the gear 50, do not extend fully around the circumference of the grooves, as shown in FIG. 5.

Each section, 72a and 72b, is connected to a drive rod a and 75b, respectively, as for instance, by means of the threaded portions 74a and 74b on the respective rods and the threaded holes 74c and 74d in the respective retaining ring sections, as clearly shown in FIGS. 3 and 7. The drive rods 75a and 75b are slidably contained in bored holes 76a and 76b, respectively in the housing 32, FIG. 3, so as to slide vertically therein. Each of the threaded portions of the drive rods passes through a yolk 77. Each rod is pinned by means of the pins 78a and 78b, respectively between the clevis-type ears a and 80b at each end of the yolk 77, as shown in FIGS. 3, 4 and 7. The clevis slot is sufficient so that there is no interference between the yolk 77 and the drive rods when the yolk is in the position shown in FIG. 4. The pins 78a and 78b are fixed in the clevis ears, but pass through clearance holes 7911 and 79b in the drive rods, so as to be rotatable therein.

A slot 81 is provided in the arc of the yolk 77 and clearance holes 82a and 82b are disposed within the arcuatelimits of the slot 81 equidistant from the pinned connections at 80a and 80b. Shouldered machine screws 83a and 83b are passed through the clearance holes, as shown in FIGS. 2 and 7, and are fastened to the plate 40. The shouldered portion of the screws provides a vertical clearance between the retained portion of the yolk 77 and the heads of the screws. This arrangement provides for a pivot for the yolk 77, so that it may assume a position such as that shown in FIG. 4.

A similar pivot is provided by the shouldered screw 84 which passes through the clearance hole 85 in the slot 86 of the actuating ring 89, FIGS. 7 and 2 and 4, so that the actuating ring 89 may assume the position shown in FIG. 4. The actuating ring 89 is pin connected to the yolk 77 by means of pins 90a and 90b, which pass through clearance holes in the yolk and are fixed in the actuating ring, so that the yolk 77 may be rotated with respect to the actuating ring 89, as shown in FIG. 4.

The actuating ring 89 is lifted to the position shown in FIG. 4 by means of the hydraulic piston mechanism shown in FIG. 2. It is to be noted that when the ring 89 is lifted, as shown in FIGS. 3 and 4, both the ring 89 and the yolk 77, as well as the retaining rings 72a and 7211 are prevented from rotation by their connection to the actuating rods 75a and 75b, however, the gear 50 may be rotated since it is slidably engaged with the retaining rings 72a and 72b by means of the lips 73a and 73b and the groove 71.

Referring to FIG. 2, the piston 93 is shown disposed in a cylinder 94, which communicates with the hydraulic fluid passages 24 and 28 in the housing 32. The piston rod 95 extends through a bushing 96 which is fastened in the cylindrical hole 97 in the housing 32 by means of the threaded portion 98. An O-ring seal 99 is provided between the hole 97 and the bushing in the cylinder 94. A sliding fit is provided between the piston rod 95 and the bushing 96. The end of the cylindrical hole 97 is capped by the plate 40 which has a recess 100 therein. Spaced along the piston rod 95 is an annular stop 101 which is in sliding engagement with the cylindrical hole 97 and is suitably aflixed to the piston rod 95 as by means of the set screw 102. Between the stop 101 and the bushing 96, there is a spring 103, and between the stop 101 and the plate 40 there is a similar spring 104. The springs 103 and 104 act on the stop 101 andtherefore on the piston 93 to equalize the position of the piston 93 when there is no fluid flow in the cylinder 94, so that it is disposed in the cylinder 94 between the port 105 in the wall of the cylinder 94 which is at the end of the passage 28 and the port 106 in the wall of the cylinder 94 which is at the end of the passage 24, as shown in FIG. 2. The end of the piston rod extends into the small chamber 108 in the fitting 109. At the end of the rod 95 there is an outwardly extending cap 107. The fitting 109 is disposed in sliding engagement with the plate 40 in the hole 110. The fitting 109 has an upwardly extending flange 111 thereon which has a laterally extending portion 112. The upwardly extending portion 111 abuts against the axially extending inner wall 113 of the actuating ring 89. The laterally extending portion 112 extends into the slot 114 in the upper radial surface of the actuating ring 89, as shown in FIGS. 2, 4 and 7. The upper surface 115 of the body of the fitting 109 extends beneath the lower radial surface of the actuating ring 89.

In operation, the engines of the vessel supply power to the pump 10 which in turn draws hydraulic fluid from the reservoir 14 and pumps it under pressure through the valve 17. The operator of the vessel in the cockpit controls the position of the valve by means of the handle 17a. When he desires to raise the sail of the boat, he adjusts the valve 17, so that pressure fluid flows in the conduit 20 to the fluid inlet passage 23 in the capstan housing 32. Fluid passes through the inlet passage 23 into the reversible hydraulic motor 35 and turns the motor which in turn turns the shaft and capstan drum 31 in a counterclockwise direction. As the capstan drum rotates in a counterclockwise direction, it winds up the halyard of the sail which in turn begins to pull the sail to the top of the mast. Referring again to FIG. 2, the hydraulic fluid as it passes out of the motor, passes through the port 27 and the passage 28 and into the cylinder 94 through the port 105, and pushes down on the piston 93 in the cylinder 94 and from there passes out of the port 106 through the hydraulic passage 24 and conduit line 21 to the valve 17 from which it is returned to the reservoir 14. When the piston 93 is pushed down to the full throttle position shown in phantom in FIG. 2, it clears the port 106 in the cylinder 94, and the cap 107 at the end of the piston rod 95 will rest against the lower end of the fitting 109 in the chamber 108.

The operator can control the height of the sail at any position by adjusting the valve 17. In its neutral position hydraulic fluid will be by-passed through the valve and returned directly to the reservoir without going through the motor. With no fluid passing through the motor 35 the ratchet mechanism 60 will prevent the load on the halyard from turning the capstan drum 3-1 and dropping the sail, since the ratchet mechanism, when engaged, is fixedly connected to the housing which in turn is connected to the boat. Likewise, if the hydraulic system should fail while the sail is being raised, the ratchet mechanism 60 will prevent the sail from falling.

:-When the sail is raised to its highest position, the halyard will be pulled taught, resulting in an increased pressure in the hydraulic lines. A pressure relief valve is provided in a by-pass line 121 to the reservoir 14, to relieve the excess pressure in the hydraulic system in the event that the operator fails to move the valve 14 to its neutral position.

When it is desired to lower the sail in a controlled manner, the operator adjusts the position of the valve 17 from neutral to reverse, so that now fluid is flowing through the conduit 21 and into the inlet passage 24 in the housing. From the inlet passage 24 it will pass into the cylinder 94. It is to be noted at this point, that when the operator has switched from the forward position on the valve to the reversed position on the valve in order to reverse the motor, the valve first passes through a neutral position, that is, a position in which no fluid is passing through the motor. In this position the springs 103 and 104 will return the piston 93 to its neutral position between the ports 105 and 106 in the cylinder 94. Thus, when the operator has switched to the reversed position, the hydraulic fluid passing into the inlet conduit 24 and from there through the port 106 into the cylinder 94, will contact the lower surface of the piston 93 and push it upwards so that it at least partially exposes the port 105, and the fluid will then proceed through the port 105 and the passage 28 and into the motor 35 reversing the motors direction. The fluid passing out of the motor 35 will pass out of the passage 23 and through the conduit to the valve 17 and then to the reservoir 14. Assuming that a moderate speed is desired in lowering the sail, the operator adjusts the valve 17 to somewhat less than full throttle in reverse. Fluid passing into the cylinder 94 at a reduced pressure, raises the piston so that it partially exposes the port 105, i.e. the full upward travel of the piston in the cylinder is not completed. The piston 93 having been pushed up will raise the gear 50 and ratchet mechanism 60. The cap 107 of the piston rod 95 abuts against the fitting 109, when the rod is in the neutral position. When the rod is raised, it will exert a force against the actuating ring 89. The actuating ring will in turn transmit a proportional vertically upward (FIG. 3) force through the pins 90a and 90b to the yolk 77, since the actuating ring is pivoted. The yolk 77 in turn will transmit a proportional vertically upward force through the pins 78a and 78b to the actuating rods 75a and 7512, since the yolk is pivoted. As the piston 93 rises in the cylinder 94, the position of the parts just described, would be that in FIG. 4, as shown in part by the alternate position of the gear 50 and ring 72b shown in phantom. The actuating rods being screwed into the split retaining rings 72a and 72b, will exert a force against these rings and will raise the gear 50. The portion 61 of the ratchet mechanism which is aifixed to the gear, will disengage from its complimentary portion 68 which is affixed to the plate 40, and allow the drum to turn in the reverse direction, i.e., clockwise FIG. 3. The gear will be only partially disengaged from the drum 31, as shown by the phantom position of the gear in FIG. 4. The motor being driven in the reversed direction as the weight of the sail pulls on the halyard, will control the rate of descent by controlling the turning movement of the drum 31.

Where it is desired to let the sail fall of its own weight, the gear can be completely disengaged from the drum 31 and the drum will spin freely on the housing. This is accomplished by continuing to raise the piston 93 by opening the valve 17 all the way in reverse allowing full throttle pressure fluid to enter the cylinder 94, and drive the piston upward all the way. The position of the gear in such a situation, is shown in FIG. 3, where the gear 50 occupies the space between the inner radial surface of the drum 31 and the mating gear portion 53 of the drum. The motor 35 in this case is turning, but there is no connection between the motor and the drum, so that the halyard can freely unwind from the drum.

With the sail down, the halyard is limp and no turning force is exerted on the drum. The gear is in the full raised or disengaged position. The operator may adjust the valve 17 to the neutral position where fluid is bypassed to the reservoir 14 and no fluid enters the motor 35. In this position the springs 103 and 104 will return the piston to its neutral position in the cylinder between the ports 105 and 106, as shown in FIG. 2. The vertical space provided in the fitting chamber 108 is of such a height that the piston cap 107 will return to the neutral position without pulling down on the fitting 109. Thus, the gear 50 will remain in the space between the teeth 53 and the inner radial surface of the capstan drum.

When the operator wishes to raise the sail once again, he moves the valve 17 to the forward position and fluid once again flows into the motor 35 to rotate it in a counterclockwise direction. As the fluid flows out of the motor and through the port 105, it depresses the piston and proceeds through the cylinder 94 and out through the port 106. In so doing, the piston 93 withdraws the fitting 109 by virtue of the cap 107 exerting a downward force against the bottom of the fitting chamber 108. The outwardly extending flange portion 112 of the fitting 109 engages the slot 114 in the radial face of the actuating ring 89 thereby drawing the actuating ring down. Since the ring is pivoted, it exerts a proportional downward force on the pins a and 90b which in turn exerts a proportional downward force on the yolk 77 which likewise is pivoted. A proportional downward force is exerted against the pins 78a and 7817, thereby withdrawing the rods 75a and 75b and their attached split rings 72a and 72b. The rings by virtue of their lip 73a and 73b engaging the annular groove 71 of the gear body will pull the gear 50 back into engagement with the internal gear teeth 53 on the drum.

To enable the gear teeth 52 to mesh easily with the teeth 53 on the drum, the gear teeth are beveled sharply to almost a point at one end, as shown at A and B in FIGS. 4 and 9. The corresponding teeth on the internal gear are beveled at the upper ends thereof, so that in a practical sense, the gears will slide together relatively easily. (See FIG. 9.) The fluid passes through the motor first causing a slight angular degree of travel by the gear 50 prior to engaging the drum. However, since the vertical space between the gear teeth 52 on the gear 50 and the teeth 53 on the drum 31 is such as to provide only a small clearance space, it has been found that the gears will mesh smoothly.

The mechanical portion of the clutch mechanism is shown in greater detail in FIGS. 2, 3, 6, and 7. This. portion of the clutch mechanism engages the lower ends of the rods 75a and 75b. Each of said ends is slotted, as at 122a and 122b, and 123a and 123b, and there is disposed between the slots a follower 125a and 12522 positioned at an angle to the axis of the rod. The lower flat surface 126a and 126b, respectively of each follower is disposed to contact and slide on the angled flat surfaces 127a and 127b, respectively of the cam ring 128 (see FIGS. 2 and 7). The cam ring 128 is disposed in the recessed slot 129 in the base 34 of the housing 32. It fits in the slot so as to be able to turn in both directions therein with a sliding rotational movement. The cam ring 128 has a slot 130 in the base thereof extending over a large portion of said base (as shown in FIGS. 6 and 7) the slot 130 being formed so that the surface 131 of the cam ring is contiguous with the upper surface 132a of the lateral passage 132 in the base of the housing and is substantially a continuation thereof. A nut-like fitting 135 is positioned to slide in said lateral passage 132 and has a pin 136 thereon, which is disposed in a hole 137 in the cam ring 128 for rotation therein. A plate 133 is securely fastened to the base 34 of the housing 32 to axially retain the cam ring 128 in the slot 129. The upper surface 134 of the plate 133 forms the lower wall of the lateral passage 132, so that the fitting 135 slides thereon. The nut-like fitting 135 has a threaded hole 138 laterally therethrough, in which there is disposed a screw 139 in threaded engagement therewith. The head 140 of the screw 139 abuts against the shoulder 141 of the counterbore 142 in the base of the housing. The shank 143 of the screw 139 passes through a clearance hole 144. The shank 143 of the screw has an annular groove 145 therein which is engaged by a snap washer 146, which washer is disposed in slots 147 and 148 on either side of the lateral passage 132. The shank of the screw can turn freely in the snap washer 146, but the snap washer 146 retains the screw 139 and prevents lateral movement along the passage 132.

It will be apparent from what has been said with respect to the aforementioned structure, that when one turns the screw 139 by hand, for example, by means of a tool engaged in the head 140 thereof, the threaded engagement in the nut-like fitting 135 with the screw 139, will cause the fitting to move laterally along the shank of the screw. There will be a slight arcuate motion which will cause the screw to move transversely in the lateral passage 132. The passage is wide enough to permit a full range of transverse movement necessary for operation of the actuating rods 75a and 75!).

Assuming the gear 50 and the drum 31 are in their normal operating position for raising the sail, as shown 9 in FIG. 2, it will be noted that the slots 150a and 150b in which the cam followers ride are of such a height that when the hydraulic portion of the mechanism is functioning to raise and lower the gear 50, the cam followers will move freely up and down, and will not interfere with the action. Should the hydraulic mechanism fail for any reason, and should it become necessary to lower the sail, the mechanical mechanism just described can be used to disengage the gears and allow the sail to fall freely. Thus, were the screw 139 to be turned in a clockwise direction (when viewed from the head 140) the fitting 135 would advance along the screw 139 toward the head 140 of the screw, and the cam ring 128 would be rotated counterclockwise (when viewed from the bottom FIG. 6). As it is rotated counterclockwise (referring to FIG. 2, the motion would be left to right) the lower flat surface 126a of the follower 125a will slide up the angled flat surface 127a of the cam ring 128. A similar action will occur with the nearer cam surface 127b shown in FIG. 7 and its corresponding follower surface 126b on rod 75b. Thus,

both rods will be raised simultaneously and to the same vertical height. In so doing, the ratchet mechanism 60 will first be disengaged and then as the cam ring 128 is rotated further, the gears will be disengaged, as previously explained in connection with the hydraulic portion of the clutch mechanism.

The mechanical portion of the clutch mechanism can be used to retract the rods 75a and 75b and thereby bring the gears into engagement. The screw 139 in the base 34 of the housing 32 can be rotated manually in a counterclockwise direction (when viewed from the head 140). This will cause the fitting 135 to advance along the screw toward the end thereof remote from the head 140 and thereby rotate the cam ring 128 in its slot 129 in the base of the housing in a clockwise direction (when viewed from the bottom as in FIG. 6). As this occurs the upper flat angled surfaces 151a and 151b of the cam ring 128 will engage the upper surfaces 152a and 15212, respectively of the followers 125a and 125b, and the followers will be urged down the cam surfaces thereby withdrawing the rods 75a and 75b and lowering the gear 50 into engagement with the drum 31 as shown in FIG. 2.

It will be understood that various changes in the details, materials and arrangements of parts which have been herein described and illustrated in order to explain the nature of this invention, may be made by those skilled in the art within the principle and scope of the invention as expressed in the following claims.

It will be further understood that the Abstract of the Disclosure set forth above is intended to provide a nonlegal technical statement of the contents of the disclosure in compliance with the Rules of Practice in the United States Patent Oflice, and is not intended to limit the scope of the invention described and claimed herein.

What is claimed is:

1. In a hydraulically operated capstan system for raising and lowering a sail on a sail boat, said system having a housing attached to said boat, a reversible hydraulic motor fixedly mounted to said housing, a drum mounted for rotation about said hydraulic motor and said housing and coupled to saidmotor for taking up and playing out a halyard therefrom, said halyard being attached to said sail, said motor having a pair of hydraulic supply and return lines connected thereto, said lines being connected to a source of hydraulic fluid'under pressure located remotely from said motor and having a control valve connected to said hydraulic supply and return lines between said source of pressure fluid and said motor for selectively admitting and reversing the flow of hydraulic pressure fluid through said hydraulic lines whereby said motor may be driven in a forward or reverse direction, the improvement comprising:

(a) a gear means disposed on the inner surface of said drum;

(b) a gear mounted on the shaft of said motor for rotation therewith and axially slidable thereon, said gear being axially slidable into and out of engagement with said gear means;

(c) actuating means disposed in one of said hydraulic supply and return lines to be actuated by the hydraulic pressure fluid therein and connected to said gear to move said gear axially along said shaft to positions of engagement and non-engagement with said gear means on said drum, whereby said sail may be raised and lowered in a controlled manner by remotely controlling the flow of pressure fluid into and out of said motor, and said gear may be disengaged from said drum by remotely controlled hydraulic means to permit said sail to freely fall.

2. An apparatus as in claim 1 wherein:

(a) ratchet means connected to said gear and said housing to permit said drum to be rotated only in one direction when said gear is in full engagement with said drum;

(b) said actuating means coacting with said gear to disengage said ratchet means in response to controlled pressure fluid flow to permit said drum to be rotated in either direction in a controlled manner by said motor.

3. An apparatus as in claim 1 wherein:

(a) a pair of actuating rods disposed in sliding engagement with said housing, each of said rods being fixedly connected at one end thereof to said gear;

(b) each of said rods having a cam at the other end thereof remote from said fixed connection with said gear;

(c) a cam ring disposed in the base of said housing for sliding rotation about the axis of said motor shaft;

(d) follower means formed in said cam ring for engagement with said cams to raise or lower said rods in response to rotation of said ring;

(e) mechanical means disposed in the base of said housing and in engagement with said cam ring to permit said ring to be rotated by hand operation of said mechanical means whereby said gear may be moved axially along said shaft to positions of engagement and non-engagement with said gear means on said drum.

4. An apparatus as in claim 3 wherein: ratchet means connected to said gear and said housing to permit said drum to be rotated only in one direction when said gear is in full engagement with said drum.

5. In a hydraulically operated capstan, having a drum mounted on a housing for rotation about a reversible hydraulic motor fixedly connected to said housing and disposed within said drum in engagement therewith for rotating said drum, the improvement comprising:

(a) a ratchet means connected to said hydraulic motor and said housing to permit rotation of said drum in one direction only;

(b) means connected to said hydraulic motor for supplying and returning hydraulic fluid under pressure comprising, a source of hydraulic fluid under pressure located remotely from said motor, hydraulic supply and return lines connected between said source of pressure fluid and said motor, and a control valve connected to said hydraulic supply and return lines between said source of pressure fluid and said motor for selectively admitting and reversing the flow of hydraulic pressure fluid through said hydraulic lines;

(c) actuating means connected to said last mentioned means and said ratchet means and responsive to the flow of pressure fluid to disengage said ratchet means and permit said .drum to be rotated in either direction; and

(d) connecting means between said motor and said said drum for rotating said drum in response to the rotation of said motor comprising:

(1) a shaft extending from said motor;

(2) gear means disposed on the inner surface of said drum;

(3) a gear mounted on the shaft of said motor for rotation therewith and axially slidable thereon, said gear being axially slidable into and out of engagement with said gear means;

(e) said ratchet means connected to said gear and said housing to permit said gear to be rotated in only one direction when said gear is fully engaged with said gear means on said drum.

6. The invention of claim 5 wherein said actuating means comprises:

(a) hydraulic piston and cylinder means disposed in one of said hydraulic supply and return lines to be actuated by the hydraulic pressure fluid therein; and

(b) linkage means connecting said piston and cylinder means with said gear and said ratchet means to move said gear axially along said shaft in response to the flow of hydraulic fluid in said fluid supply and return lines whereby said ratchet means may be disengaged to permit rotation of said drum in either direction, and said gear may be moved to positions of full and partial engagement with said gear means on said drum and to a position of complete disengagement from said gear means on said drum.

7. The invention of claim 6 wherein there is provided a collar forming one end wall of said cylinder, a piston rod connected at one end of said piston, said piston rod being disposed to slide through said collar, a stop fixedly connected to said piston rod without said cylinder, a

spring disposed between said collar and said stop, a cylindrical chamber formed within said housing, said collar forming one end wall of said chamber, a spring disposed between said stop and the other end Wall of said chamber, said fluid supply line communicating with said cylinder in two ports axially spaced from one another along the walls of said cylinder, said springs cooperating to position said piston between said ports when no hydraulic fluid is flowing through said line, said housing having a passage communicating with one end of said cylindrical chamber remote from said collar, a fitting disposed to slide in said passage, said fitting having a chamber formed therein, the end of said piston rod remote from said piston disposed in said fitting chamber, a cap disposed on said end of said piston rod in said chamber disposed to engage either end of said chamber in said fitting upon appropriate movement of said piston rod, an actuating ring disposed on said housing about said shaft, said ring being pivotally connected to said housing, said fitting being disposed to engage said ring and raise and lower the ring upon appropriate movement of said piston, a yolk connected for rotation at the ends thereof to said ring and pivotally connected at the center thereof to said housing, said yolk being disposed to be pivotally raised and lowered in response to the pivotal raising and lowering of the actuating ring, said yolk having clevis means disposed in either end thereof, a pair of actuating rods disposed in sliding engagement with said housing, each of said rods Ebeing pivotally connected to one of said clevis means, .said actuating rods being fixedly connected to said gear, whereby said gear may be axially positioned upon appropriate movement of said piston in response to the flow of pressure fluid in said line.

8. The invention of claim 7 wherein said actuating rods have cams at the ends thereof remote from said fixed connections with said gear, said cams disposed to ride on followers formed in a cam ring, said cam ring disposed in the base of said housing for sliding rotation about the axis of said shaft whereby said rods will be uniformly raised or lowered depending on a direction of rotation of said ring, mechanical means disposed in the base of said housing and in engagement with said cam ring to permit hand operation of said ring to rotate said ring.

References Cited UNITED STATES PATENTS 167,693 10/1875 Russell 254-150 1,146,339 7/1915 Matthews 254l50 2,671,880 3/1954 Symonds 254-187 3,339,894 9/1967 Millard 254-15O RICHARD E. AEGERTER, Primary Examiner. H. C. HORNSBY, Assistant Examiner. 

